WO2015111707A1 - Seal ring - Google Patents

Seal ring Download PDF

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Publication number
WO2015111707A1
WO2015111707A1 PCT/JP2015/051869 JP2015051869W WO2015111707A1 WO 2015111707 A1 WO2015111707 A1 WO 2015111707A1 JP 2015051869 W JP2015051869 W JP 2015051869W WO 2015111707 A1 WO2015111707 A1 WO 2015111707A1
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WO
WIPO (PCT)
Prior art keywords
groove
seal ring
present
circumferential direction
dynamic pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/051869
Other languages
French (fr)
Japanese (ja)
Inventor
真利 関
猛 細江
井上　秀行
雄一郎 徳永
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nok Corp
Eagle Industry Co Ltd
Original Assignee
Nok Corp
Eagle Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=53681504&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2015111707(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Nok Corp, Eagle Industry Co Ltd filed Critical Nok Corp
Priority to EP15740299.1A priority Critical patent/EP3098486B1/en
Priority to KR1020167019126A priority patent/KR20160098451A/en
Priority to US15/113,506 priority patent/US10865883B2/en
Priority to CN201580005061.XA priority patent/CN105917151A/en
Priority to JP2015559134A priority patent/JP6298834B2/en
Publication of WO2015111707A1 publication Critical patent/WO2015111707A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/441—Free-space packings with floating ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3268—Mounting of sealing rings
    • F16J15/3272—Mounting of sealing rings the rings having a break or opening, e.g. to enable mounting on a shaft otherwise than from a shaft end
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/91—O-ring seal

Definitions

  • the present invention relates to a seal ring that seals an annular gap between a shaft and a shaft hole of a housing.
  • An object of the present invention is to provide a sealing device capable of suppressing leakage of a fluid to be sealed while reducing rotational torque regardless of the rotation direction.
  • the present invention employs the following means in order to solve the above problems.
  • the seal ring of the present invention is Fluid pressure in a region to be sealed is mounted in an annular groove provided on the outer periphery of the shaft and configured to seal the annular clearance between the relatively rotating shaft and the housing so that the fluid pressure changes.
  • a seal ring for holding In the seal ring that slides against the side wall surface on the low pressure side in the annular groove On the sliding surface side that slides with respect to the side wall surface, a first groove having a constant radial width and extending in the circumferential direction, and extending from the center position in the circumferential direction of the first groove to the inner peripheral surface.
  • a dynamic pressure generating groove having a second groove for guiding the fluid to be sealed into the first groove is provided, The first groove is provided at a position within a sliding area that slides with respect to the side wall surface.
  • the fluid to be sealed is guided into the dynamic pressure generating groove. Therefore, in the range where the dynamic pressure generating groove is provided, the fluid pressure acting on the seal ring from the high pressure side cancels out the fluid pressure acting on the seal ring from the low pressure side. Thereby, the pressure receiving area of the fluid pressure with respect to the seal ring can be reduced. Further, when the seal ring slides on the side wall surface on the low pressure side in the annular groove, a dynamic pressure is generated when the fluid to be sealed flows from the first groove to the sliding portion. Thereby, the force of the direction away from a side wall surface with respect to a seal ring generate
  • the dynamic pressure generating groove includes a first groove and a second groove extending from the circumferential center of the first groove to the inner peripheral surface. Accordingly, the dynamic pressure is generated regardless of the rotation direction of the seal ring with respect to the annular groove.
  • the first groove is provided in a position that fits within a sliding area that slides with respect to the side wall surface, leakage of the fluid to be sealed can be suppressed.
  • the groove bottom of the first groove is configured to be shallower at both ends compared to the center in the circumferential direction.
  • FIG. 1 is a side view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 2 is a view of the seal ring according to the first embodiment of the present invention as viewed from the outer peripheral surface side.
  • FIG. 3 is a side view of the seal ring according to the first embodiment of the present invention.
  • FIG. 4 is a partially enlarged view of a side view of the seal ring according to the first embodiment of the present invention.
  • FIG. 5 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 6 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 7 is a schematic cross-sectional view showing a state when the seal ring according to the first embodiment of the present invention is used.
  • FIG. 8 is a schematic cross-sectional view of the seal ring according to the first embodiment of the present invention.
  • FIG. 9 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 10 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 11 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 12 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 13 is a partially enlarged view of a side view of a seal ring according to Embodiment 2 of the present invention.
  • FIG. 14 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention.
  • FIG. 15 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention.
  • FIG. 16 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention.
  • FIG. 17 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention.
  • FIG. 18 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention.
  • FIG. 19 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention.
  • the seal ring according to the present embodiment is used for sealing an annular gap between a relatively rotating shaft and a housing in order to maintain hydraulic pressure in a transmission such as an AT or CVT for automobiles. It is used.
  • high pressure side means a side that becomes high when differential pressure occurs on both sides of the seal ring
  • low pressure side means that differential pressure occurs on both sides of the seal ring. This means the side that is at low pressure.
  • FIGS. 1 is a side view of a seal ring according to Embodiment 1 of the present invention.
  • FIG. 1 shows a side surface of the seal ring opposite to the sliding surface.
  • FIG. 2 is a view of the seal ring according to the first embodiment of the present invention as viewed from the outer peripheral surface side.
  • FIG. 3 is a side view of the seal ring according to the first embodiment of the present invention.
  • FIG. 3 shows the side surface of the seal ring on the sliding surface side.
  • FIG. 4 is a partially enlarged view of a side view of the seal ring according to the first embodiment of the present invention. 4 is an enlarged view of the vicinity of the abutment portion 110 in FIG. FIG.
  • FIG. 5 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • 5 is a cross-sectional view taken along line AA in FIG.
  • FIG. 6 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention.
  • 6 is a cross-sectional view taken along the line BB in FIG.
  • FIG. 7 is a schematic cross-sectional view showing a state when the seal ring according to the first embodiment of the present invention is used.
  • the seal ring in FIG. 7 is an AA cross-sectional view in FIG. 8 to 12 are schematic cross-sectional views of the seal ring according to Embodiment 1 of the present invention.
  • 8 to 12 are CC sectional views in FIG.
  • the seal ring 100 is mounted in an annular groove 210 provided on the outer periphery of the shaft 200, and rotates relative to the shaft 200 and the housing 300 (the inner periphery of the shaft hole through which the shaft 200 in the housing 300 is inserted.
  • the annular gap between the first and second surfaces is sealed.
  • the seal ring 100 maintains the fluid pressure in the seal target region configured so that the fluid pressure (hydraulic pressure in the present embodiment) changes.
  • the fluid pressure in the region on the right side in FIG. 7 is configured to change, and the seal ring 100 plays a role of maintaining the fluid pressure in the region to be sealed on the right side in the diagram. Yes.
  • FIG. 7 shows a state in which the fluid pressure on the right side in the drawing is higher than the fluid pressure on the left side.
  • H high pressure side
  • L low pressure side
  • the seal ring 100 is made of a resin material such as polyetheretherketone (PEEK), polyphenylene sulfide (PPS), polytetrafluoroethylene (PTFE). Further, the peripheral length of the outer peripheral surface of the seal ring 100 is configured to be shorter than the peripheral length of the inner peripheral surface of the shaft hole of the housing 300 and is configured not to have a tightening allowance. Accordingly, the outer peripheral surface of the seal ring 100 can be separated from the inner peripheral surface of the housing 300 in a state where fluid pressure is not acting.
  • PEEK polyetheretherketone
  • PPS polyphenylene sulfide
  • PTFE polytetrafluoroethylene
  • the seal ring 100 is provided with an abutment portion 110 at one place in the circumferential direction.
  • a dynamic pressure generating groove 120 is provided on the sliding surface side of the seal ring 100.
  • the seal ring 100 according to the present embodiment has a configuration in which the above-described joint portion 110 and a plurality of dynamic pressure generating grooves 120 are formed on an annular member having a rectangular cross section.
  • this is merely an explanation of the shape, and does not necessarily mean that the annular member having a rectangular cross section is used as a material, and the joint portion 110 and the plurality of dynamic pressure generating grooves 120 are formed. .
  • a plurality of dynamic pressure generating grooves 120 may be obtained by cutting after forming a joint portion 110 in advance, and the manufacturing method is not particularly limited.
  • the joint portion 110 employs a so-called special step cut that is cut in a step shape when viewed from either the outer peripheral surface side or both side wall surfaces. Since the special step cut is a known technique, a detailed description thereof is omitted, but it has a characteristic of maintaining a stable sealing performance even if the circumference of the seal ring 100 is changed due to thermal expansion and contraction.
  • the special step cut is shown as an example of the abutment portion 110, but the abutment portion 110 is not limited to this, and a straight cut, a bias cut, a step cut, or the like can also be adopted. Note that when a low-elasticity material (such as PTFE) is employed as the material of the seal ring 100, the end portion may be provided without providing the joint portion 110.
  • a low-elasticity material such as PTFE
  • a plurality of dynamic pressure generating grooves 120 are provided at equal intervals over the entire circumference of the seal ring 100 on the sliding surface side except for the vicinity of the joint portion 110 (see FIG. 3).
  • the plurality of dynamic pressure generating grooves 120 are provided to generate dynamic pressure when the seal ring 100 slides with respect to the side wall surface 211 on the low pressure side in the annular groove 210 provided in the shaft 200.
  • the dynamic pressure generating groove 120 has a first groove 121 having a constant radial width and extending in the circumferential direction, and extends from the center position in the circumferential direction of the first groove 121 to the inner peripheral surface. And a second groove 122 that guides the light into the first groove 121.
  • the first groove 121 is provided at a position that fits in the sliding region X that slides with respect to the low-pressure side wall surface 211 in the annular groove 210 (see FIG. 7). Further, the groove depth of the first groove 121 is configured to be constant in the radial direction (see FIGS. 5 and 7). And about the groove depth of the 1st groove
  • FIG. 8 shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward both sides in a planar shape from the center in the circumferential direction.
  • FIG. 9 shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a curved shape from the center in the circumferential direction.
  • FIG. 10 shows an example in which the groove bottom of the first groove 121 becomes shallower toward both sides stepwise from the center in the circumferential direction.
  • FIG. 11 shows an example in which the groove bottom of the first groove 121 becomes shallower toward the both sides in a stepwise manner from the center in the circumferential direction, and the stepped portion is formed of an inclined surface.
  • the groove bottom of the first groove 121 is configured such that both ends are shallower than the center in the circumferential direction, so that dynamic pressure can be generated more effectively by the wedge effect.
  • channel 121 in a present Example is set so that it may become 50 micrometers or less even in the deepest part.
  • FIG. 7 shows a state in which the engine is started and a differential pressure is generated via the seal ring 100 (a state in which the pressure on the right side in the drawing is higher than the pressure on the left side).
  • the seal ring 100 is in close contact with the low-pressure side (L) side wall surface 211 of the annular groove 210 and the inner peripheral surface of the shaft hole of the housing 300.
  • the annular gap between the relatively rotating shaft 200 and the housing 300 is sealed, and the fluid pressure in the region to be sealed (the region on the high pressure side (H)) configured to change the fluid pressure. Can be held.
  • the shaft 200 and the housing 300 are relatively rotated, the shaft 200 slides between the side wall surface 211 on the low pressure side (L) of the annular groove 210 and the seal ring 100.
  • dynamic pressure is generated when the fluid to be sealed flows out from the dynamic pressure generating groove 120 provided on the sliding surface side surface of the seal ring 100 to the sliding portion.
  • the seal ring 100 rotates in the clockwise direction in FIG.
  • the fluid to be sealed flows out from the end portion of the first groove 121 on the counterclockwise direction side to the sliding portion.
  • the seal ring 100 rotates counterclockwise in FIG. 3 with respect to the annular groove 210, the fluid to be sealed flows out from the end portion on the clockwise direction side of the first groove 121 to the sliding portion. .
  • the dynamic pressure generating groove 120 includes a first groove 121 and a second groove 122 extending from the circumferential center of the first groove 121 to the inner peripheral surface. Accordingly, the dynamic pressure is generated regardless of the rotation direction of the seal ring 100 with respect to the annular groove 210.
  • the first groove 121 is provided at a position within the sliding region X that slides with respect to the side wall surface 211, leakage of the fluid to be sealed can be suppressed.
  • the groove bottom of the first groove 121 is configured to be shallower at both ends compared to the center in the circumferential direction, the above-described dynamic pressure is reduced by the wedge effect. It can be generated effectively.
  • FIGS. 8 and 9 when a configuration in which the groove bottom of the first groove 121 gradually becomes shallower from the center in the circumferential direction toward both sides is adopted, Even if the side surface wears over time, the wedge effect can be stably exhibited.
  • Example 2 13 to 19 show a second embodiment of the present invention.
  • the depth of the portion connected to the second groove in the first groove is the same as the depth of the second groove, and the portion connected to the second groove in the first groove.
  • the structure at the time of constructing deeper than the depth of the part other than is shown. Since other configurations and operations are the same as those in the first embodiment, the same components are denoted by the same reference numerals and description thereof is omitted.
  • FIG. 13 is a partially enlarged view of a side view of the seal ring according to the second embodiment of the present invention, which corresponds to FIG. 4 in the first embodiment.
  • 14 to 19 are schematic sectional views of a seal ring according to Embodiment 2 of the present invention. 14 to 19 are CC sectional views in FIG.
  • the dynamic pressure generating groove 120 includes a first groove 121 having a constant radial width and extending in the circumferential direction, and an inner circumference from a center position in the circumferential direction of the first groove 121.
  • the second groove 122 extends to the surface and guides the fluid to be sealed into the first groove 121.
  • first groove 121 is also provided at a position that fits within the sliding region X that slides with respect to the low-pressure side wall surface 211 in the annular groove 210 as in the case of the first embodiment. (See FIG. 7). Further, the groove depth of the first groove 121 is the same as that of the first embodiment in that the depth is configured to be constant in the radial direction.
  • the depth of the portion 121X of the first groove 121 connected to the second groove 122 is the same as the depth of the second groove 122, and the first groove 121 is configured to be deeper than the depth of the portion 121 ⁇ / b> Y other than the portion connected to the second groove 122.
  • channel 121 various structures can be employ
  • FIGS. 14 to 19 show various examples in which the groove bottom of the first groove 121 is configured to be shallower at both ends compared to the center in the circumferential direction.
  • FIG. 14 is a modification of the example shown in FIG. 8 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a planar shape from the center in the circumferential direction. .
  • channels 121 is deeper than the other part 121Y.
  • FIG. 15 is a modification of the example shown in FIG.
  • FIG. 9 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a curved shape from the center in the circumferential direction. .
  • channels 121 is deeper than the other part 121Y.
  • FIG. 16 is a modification of the example shown in FIG. 10 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 becomes shallower toward both sides stepwise from the center in the circumferential direction.
  • channels 121 is deeper than the other part 121Y.
  • FIG. 17 is a modification of the example shown in FIG. 8 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a planar shape from the center in the circumferential direction. . And the depth of the part 121X connected with the 2nd groove
  • FIG. 18 is a modification of the example shown in FIG.
  • FIG. 9 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a curved shape from the center in the circumferential direction. .
  • channels 121 is deeper than the other part 121Y.
  • FIG. 19 is a modification of the example shown in FIG. 10 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 becomes shallower toward both sides stepwise from the center in the circumferential direction.
  • channels 121 is deeper than the other part 121Y. Moreover, it is comprised so that the groove bottom of the part 121X connected with the 2nd groove
  • the depth of the portion 121Y other than the portion connected to the second groove 122 in the first groove 121 is set to be 50 ⁇ m or less even at the deepest portion.
  • the depth of the second groove 122 in the dynamic pressure generating groove 120 and the depth of the portion 121X of the first groove 121 connected to the second groove 122 can be increased. Therefore, the dynamic pressure generation effect by the dynamic pressure generation groove 120 can be enhanced.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)

Abstract

Provided is a sealing device configured so that, irrespective of a rotational direction, rotational torque can be reduced and the leakage of sealed fluid can be prevented. A seal ring (100) slides relative to the low pressure-side sidewall surface of an annular groove. The seal ring (100) has, provided in the slide surface thereof which slides relative to the sidewall surface, a dynamic pressure generation groove (120) having: a first groove (121) circumferentially extending with a constant radial width; and a second groove (122) extending from the circumferential center of the first groove (121) up to the inner peripheral surface thereof and conducting sealed fluid into the first groove (121). The seal ring (100) is characterized in that the first groove (121) is provided at a position within a slide region sliding relative to the sidewall surface.

Description

シールリングSeal ring

　本発明は、軸とハウジングの軸孔との間の環状隙間を封止するシールリングに関する。 The present invention relates to a seal ring that seals an annular gap between a shaft and a shaft hole of a housing.

　自動車用のＡｕｔｏｍａｔｉｃ　Ｔｒａｎｓｍｉｓｓｉｏｎ（ＡＴ）やＣｏｎｔｉｎｕｏｕｓｌｙ　Ｖａｒｉａｂｌｅ　Ｔｒａｎｓｍｉｓｓｉｏｎ（ＣＶＴ）においては、油圧を保持させるために、相対的に回転する軸とハウジングとの間の環状隙間を封止するシールリングが設けられている。近年、環境問題対策として低燃費化が進められており、上記シールリングにおいては、回転トルクを低減させる要求が高まっている。そこで、従来、シールリングの摺動面側に密封対象流体を導く溝を設ける技術が知られている（特許文献１及び２参照）。 Automatic Transmission (AT) and Continuously Variable Transmission (CVT) for automobiles are provided with a seal ring that seals the annular gap between the relatively rotating shaft and the housing in order to maintain the hydraulic pressure. . In recent years, fuel efficiency has been reduced as a countermeasure for environmental problems, and there is an increasing demand for reducing the rotational torque in the seal ring. Therefore, conventionally, a technique for providing a groove for guiding a fluid to be sealed on the sliding surface side of the seal ring is known (see Patent Documents 1 and 2).

　しかしながら、回転方向に拘わらず、回転トルクを低減させることが望まれるなど、未だ改良の余地がある。また、シールリング本来の機能である密封対象流体の漏れを抑制させる必要もある。 However, there is still room for improvement, such as desiring to reduce rotational torque regardless of the rotational direction. It is also necessary to suppress leakage of the fluid to be sealed, which is the original function of the seal ring.

実開平０３－０８８０６２号公報Japanese Utility Model Publication No. 03-080662 国際公開第２０１１／１０５５１３号公報International Publication No. 2011/105513

　本発明の目的は、回転方向に関係なく、回転トルクを低減させつつ、密封対象流体の漏れを抑制することが可能な密封装置を提供することにある。 An object of the present invention is to provide a sealing device capable of suppressing leakage of a fluid to be sealed while reducing rotational torque regardless of the rotation direction.

　本発明は、上記課題を解決するために以下の手段を採用した。 The present invention employs the following means in order to solve the above problems.

　すなわち、本発明のシールリングは、
　軸の外周に設けられた環状溝に装着され、相対的に回転する前記軸とハウジングとの間の環状隙間を封止して、流体圧力が変化するように構成されたシール対象領域の流体圧力を保持するシールリングであって、
　前記環状溝における低圧側の側壁面に対して摺動するシールリングにおいて、
　前記側壁面に対して摺動する摺動面側には、径方向の幅が一定で周方向に伸びる第１溝と、第１溝における周方向の中央の位置から内周面に至るまで伸び、密封対象流体を第１溝内に導く第２溝とを有する動圧発生用溝が設けられており、
　第１溝は、前記側壁面に対して摺動する摺動領域内に収まる位置に設けられていることを特徴とする。 That is, the seal ring of the present invention is
Fluid pressure in a region to be sealed is mounted in an annular groove provided on the outer periphery of the shaft and configured to seal the annular clearance between the relatively rotating shaft and the housing so that the fluid pressure changes. A seal ring for holding
In the seal ring that slides against the side wall surface on the low pressure side in the annular groove,
On the sliding surface side that slides with respect to the side wall surface, a first groove having a constant radial width and extending in the circumferential direction, and extending from the center position in the circumferential direction of the first groove to the inner peripheral surface. , A dynamic pressure generating groove having a second groove for guiding the fluid to be sealed into the first groove is provided,
The first groove is provided at a position within a sliding area that slides with respect to the side wall surface.

　本発明によれば、動圧発生用溝内に密封対象流体が導かれる。そのため、動圧発生用溝が設けられている範囲においては、高圧側からシールリングに対して作用する流体圧力と低圧側からシールリングに対して作用する流体圧力が相殺される。これにより、シールリングに対する流体圧力の受圧面積を減らすことができる。また、シールリングが環状溝における低圧側の側壁面に対して摺動する際に、第１溝から摺動部分に密封対象流体が流出する際に動圧が発生する。これにより、シールリングに対して側壁面から離れる方向の力が発生する。以上のように、受圧面積が減ることと、動圧によりシールリングに対して側壁面から離れる方向に力が発生することとが相俟って、回転トルクを効果的に低減させることが可能となる。 According to the present invention, the fluid to be sealed is guided into the dynamic pressure generating groove. Therefore, in the range where the dynamic pressure generating groove is provided, the fluid pressure acting on the seal ring from the high pressure side cancels out the fluid pressure acting on the seal ring from the low pressure side. Thereby, the pressure receiving area of the fluid pressure with respect to the seal ring can be reduced. Further, when the seal ring slides on the side wall surface on the low pressure side in the annular groove, a dynamic pressure is generated when the fluid to be sealed flows from the first groove to the sliding portion. Thereby, the force of the direction away from a side wall surface with respect to a seal ring generate | occur | produces. As described above, the rotational torque can be effectively reduced by combining the reduction of the pressure receiving area and the generation of force in the direction away from the side wall surface with respect to the seal ring due to the dynamic pressure. Become.

　また、動圧発生用溝は、第１溝と、第１溝の周方向の中央から内周面に至るまで伸びる第２溝とを備える構成である。従って、環状溝に対するシールリングの回転方向に関係なく、上記の動圧が発生する。 Further, the dynamic pressure generating groove includes a first groove and a second groove extending from the circumferential center of the first groove to the inner peripheral surface. Accordingly, the dynamic pressure is generated regardless of the rotation direction of the seal ring with respect to the annular groove.

　更に、第１溝は、側壁面に対して摺動する摺動領域内に収まる位置に設けられているので、密封対象流体の漏れを抑制することができる。 Furthermore, since the first groove is provided in a position that fits within a sliding area that slides with respect to the side wall surface, leakage of the fluid to be sealed can be suppressed.

　ここで、第１溝の溝底は、周方向の中央に比べて両端側の方が浅くなるように構成されているとよい。 Here, it is preferable that the groove bottom of the first groove is configured to be shallower at both ends compared to the center in the circumferential direction.

　こうすることで、楔効果により、上記の動圧を効果的に発生させることができる。 In this way, the dynamic pressure can be effectively generated by the wedge effect.

　以上説明したように、本発明によれば、回転方向に関係なく、回転トルクを低減させつつ、密封対象流体の漏れを抑制することができる。 As described above, according to the present invention, it is possible to suppress the leakage of the fluid to be sealed while reducing the rotational torque regardless of the rotational direction.

図１は本発明の実施例１に係るシールリングの側面図である。1 is a side view of a seal ring according to Embodiment 1 of the present invention. 図２は本発明の実施例１に係るシールリングを外周面側から見た図である。FIG. 2 is a view of the seal ring according to the first embodiment of the present invention as viewed from the outer peripheral surface side. 図３は本発明の実施例１に係るシールリングの側面図である。FIG. 3 is a side view of the seal ring according to the first embodiment of the present invention. 図４は本発明の実施例１に係るシールリングの側面図の一部拡大図である。FIG. 4 is a partially enlarged view of a side view of the seal ring according to the first embodiment of the present invention. 図５は本発明の実施例１に係るシールリングの模式的断面図である。FIG. 5 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 図６は本発明の実施例１に係るシールリングの模式的断面図である。FIG. 6 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 図７は本発明の実施例１に係るシールリングの使用時の状態を示す模式的断面図である。FIG. 7 is a schematic cross-sectional view showing a state when the seal ring according to the first embodiment of the present invention is used. 図８は本発明の実施例１に係るシールリングの模式的断面図である。FIG. 8 is a schematic cross-sectional view of the seal ring according to the first embodiment of the present invention. 図９は本発明の実施例１に係るシールリングの模式的断面図である。FIG. 9 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 図１０は本発明の実施例１に係るシールリングの模式的断面図である。FIG. 10 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 図１１は本発明の実施例１に係るシールリングの模式的断面図である。FIG. 11 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 図１２は本発明の実施例１に係るシールリングの模式的断面図である。FIG. 12 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 図１３は本発明の実施例２に係るシールリングの側面図の一部拡大図である。FIG. 13 is a partially enlarged view of a side view of a seal ring according to Embodiment 2 of the present invention. 図１４は本発明の実施例２に係るシールリングの模式的断面図である。FIG. 14 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention. 図１５は本発明の実施例２に係るシールリングの模式的断面図である。FIG. 15 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention. 図１６は本発明の実施例２に係るシールリングの模式的断面図である。FIG. 16 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention. 図１７は本発明の実施例２に係るシールリングの模式的断面図である。FIG. 17 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention. 図１８は本発明の実施例２に係るシールリングの模式的断面図である。FIG. 18 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention. 図１９は本発明の実施例２に係るシールリングの模式的断面図である。FIG. 19 is a schematic cross-sectional view of a seal ring according to Embodiment 2 of the present invention.

　以下に図面を参照して、この発明を実施するための形態を、実施例に基づいて例示的に詳しく説明する。ただし、この実施例に記載されている構成部品の寸法、材質、形状、その相対配置などは、特に特定的な記載がない限りは、この発明の範囲をそれらのみに限定する趣旨のものではない。なお、本実施例に係るシールリングは、自動車用のＡＴやＣＶＴなどの変速機において、油圧を保持させるために、相対的に回転する軸とハウジングとの間の環状隙間を封止する用途に用いられるものである。また、以下の説明において、「高圧側」とは、シールリングの両側に差圧が生じた際に高圧となる側を意味し、「低圧側」とは、シールリングの両側に差圧が生じた際に低圧となる側を意味する。 DETAILED DESCRIPTION Hereinafter, embodiments for carrying out the present invention will be exemplarily described in detail with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention only to those unless otherwise specified. . The seal ring according to the present embodiment is used for sealing an annular gap between a relatively rotating shaft and a housing in order to maintain hydraulic pressure in a transmission such as an AT or CVT for automobiles. It is used. In the following description, “high pressure side” means a side that becomes high when differential pressure occurs on both sides of the seal ring, and “low pressure side” means that differential pressure occurs on both sides of the seal ring. This means the side that is at low pressure.

　（実施例１）
　図１～図１２を参照して、本発明の実施例に係るシールリングについて説明する。図１は本発明の実施例１に係るシールリングの側面図である。なお、図１は、シールリングにおける摺動面とは反対側の側面を示している。図２は本発明の実施例１に係るシールリングを外周面側から見た図である。図３は本発明の実施例１に係るシールリングの側面図である。なお、図３は、シールリングにおける摺動面側の側面を示している。図４は本発明の実施例１に係るシールリングの側面図の一部拡大図である。なお、図４は図３のうち合口部１１０が設けられている付近を拡大した図である。図５は本発明の実施例１に係るシールリングの模式的断面図である。なお、図５は図３中のＡＡ断面図である。図６は本発明の実施例１に係るシールリングの模式的断面図である。なお、図６は図３中のＢＢ断面図である。図７は本発明の実施例１に係るシールリングの使用時の状態を示す模式的断面図である。なお、図７中のシールリングは、図３中のＡＡ断面図である。図８～図１２は本発明の実施例１に係るシールリングの模式的断面図である。なお、図８～図１２は図４中のＣＣ断面図である。 Example 1
A seal ring according to an embodiment of the present invention will be described with reference to FIGS. 1 is a side view of a seal ring according to Embodiment 1 of the present invention. FIG. 1 shows a side surface of the seal ring opposite to the sliding surface. FIG. 2 is a view of the seal ring according to the first embodiment of the present invention as viewed from the outer peripheral surface side. FIG. 3 is a side view of the seal ring according to the first embodiment of the present invention. FIG. 3 shows the side surface of the seal ring on the sliding surface side. FIG. 4 is a partially enlarged view of a side view of the seal ring according to the first embodiment of the present invention. 4 is an enlarged view of the vicinity of the abutment portion 110 in FIG. FIG. 5 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 5 is a cross-sectional view taken along line AA in FIG. FIG. 6 is a schematic cross-sectional view of a seal ring according to Embodiment 1 of the present invention. 6 is a cross-sectional view taken along the line BB in FIG. FIG. 7 is a schematic cross-sectional view showing a state when the seal ring according to the first embodiment of the present invention is used. In addition, the seal ring in FIG. 7 is an AA cross-sectional view in FIG. 8 to 12 are schematic cross-sectional views of the seal ring according to Embodiment 1 of the present invention. 8 to 12 are CC sectional views in FIG.

　＜シールリングの構成＞
　本実施例に係るシールリング１００は、軸２００の外周に設けられた環状溝２１０に装着され、相対的に回転する軸２００とハウジング３００（ハウジング３００における軸２００が挿通される軸孔の内周面）との間の環状隙間を封止する。これにより、シールリング１００は、流体圧力（本実施例では油圧）が変化するように構成されたシール対象領域の流体圧力を保持する。ここで、本実施例においては、図７中の右側の領域の流体圧力が変化するように構成されており、シールリング１００は図中右側のシール対象領域の流体圧力を保持する役割を担っている。なお、自動車のエンジンが停止した状態においては、シール対象領域の流体圧力は低く、無負荷の状態となっており、エンジンをかけるとシール対象領域の流体圧力は高くなる。また、図７においては、図中右側の流体圧力が左側の流体圧力よりも高くなった状態を示している。以下、図７中右側を高圧側（Ｈ）、左側を低圧側（Ｌ）と称する。 <Configuration of seal ring>
The seal ring 100 according to the present embodiment is mounted in an annular groove 210 provided on the outer periphery of the shaft 200, and rotates relative to the shaft 200 and the housing 300 (the inner periphery of the shaft hole through which the shaft 200 in the housing 300 is inserted. The annular gap between the first and second surfaces is sealed. As a result, the seal ring 100 maintains the fluid pressure in the seal target region configured so that the fluid pressure (hydraulic pressure in the present embodiment) changes. Here, in this embodiment, the fluid pressure in the region on the right side in FIG. 7 is configured to change, and the seal ring 100 plays a role of maintaining the fluid pressure in the region to be sealed on the right side in the diagram. Yes. When the automobile engine is stopped, the fluid pressure in the seal target area is low and no load is applied. When the engine is started, the fluid pressure in the seal target area increases. FIG. 7 shows a state in which the fluid pressure on the right side in the drawing is higher than the fluid pressure on the left side. Hereinafter, the right side in FIG. 7 is referred to as a high pressure side (H), and the left side is referred to as a low pressure side (L).

　そして、シールリング１００は、ポリエーテルエーテルケトン（ＰＥＥＫ）、ポリフェニレンサルファイド（ＰＰＳ）、ポリテトラフルオロエチレン（ＰＴＦＥ）などの樹脂材からなる。また、シールリング１００の外周面の周長はハウジング３００の軸孔の内周面の周長よりも短く構成されており、締め代を持たないように構成されている。従って、流体圧力が作用していない状態においては、シールリング１００の外周面はハウジング３００の内周面から離れた状態となり得る。 The seal ring 100 is made of a resin material such as polyetheretherketone (PEEK), polyphenylene sulfide (PPS), polytetrafluoroethylene (PTFE). Further, the peripheral length of the outer peripheral surface of the seal ring 100 is configured to be shorter than the peripheral length of the inner peripheral surface of the shaft hole of the housing 300 and is configured not to have a tightening allowance. Accordingly, the outer peripheral surface of the seal ring 100 can be separated from the inner peripheral surface of the housing 300 in a state where fluid pressure is not acting.

　このシールリング１００には、周方向の１箇所に合口部１１０が設けられている。また、シールリング１００の摺動面側には動圧発生用溝１２０が設けられている。なお、本実施例に係るシールリング１００は、断面が矩形の環状部材に対して、上記の合口部１１０と複数の動圧発生用溝１２０が形成された構成である。ただし、これは形状についての説明に過ぎず、必ずしも、断面が矩形の環状部材を素材として、これら合口部１１０及び複数の動圧発生用溝１２０を形成する加工を施すことを意味するものではない。勿論、断面が矩形の環状部材を成形した後に、これらを切削加工により得ることもできる。ただし、例えば、予め合口部１１０を有したものを成形した後に、複数の動圧発生用溝１２０を切削加工により得てもよいし、製法は特に限定されるものではない。 The seal ring 100 is provided with an abutment portion 110 at one place in the circumferential direction. A dynamic pressure generating groove 120 is provided on the sliding surface side of the seal ring 100. The seal ring 100 according to the present embodiment has a configuration in which the above-described joint portion 110 and a plurality of dynamic pressure generating grooves 120 are formed on an annular member having a rectangular cross section. However, this is merely an explanation of the shape, and does not necessarily mean that the annular member having a rectangular cross section is used as a material, and the joint portion 110 and the plurality of dynamic pressure generating grooves 120 are formed. . Of course, after forming an annular member having a rectangular cross section, these can be obtained by cutting. However, for example, a plurality of dynamic pressure generating grooves 120 may be obtained by cutting after forming a joint portion 110 in advance, and the manufacturing method is not particularly limited.

　合口部１１０は、外周面側及び両側壁面側のいずれから見ても階段状に切断された、いわゆる特殊ステップカットを採用している。特殊ステップカットに関しては公知技術であるので、その詳細な説明は省略するが、熱膨張収縮によりシールリング１００の周長が変化しても安定したシール性能を維持する特性を有する。なお、ここでは合口部１１０の一例として、特殊ステップカットの場合を示したが、合口部１１０については、これに限らず、ストレートカットやバイアスカットやステップカットなども採用し得る。なお、シールリング１００の材料として、低弾性の材料（ＰＴＦＥなど）を採用した場合には、合口部１１０を設けずに、エンドレスとしてもよい。 The joint portion 110 employs a so-called special step cut that is cut in a step shape when viewed from either the outer peripheral surface side or both side wall surfaces. Since the special step cut is a known technique, a detailed description thereof is omitted, but it has a characteristic of maintaining a stable sealing performance even if the circumference of the seal ring 100 is changed due to thermal expansion and contraction. Here, the case of the special step cut is shown as an example of the abutment portion 110, but the abutment portion 110 is not limited to this, and a straight cut, a bias cut, a step cut, or the like can also be adopted. Note that when a low-elasticity material (such as PTFE) is employed as the material of the seal ring 100, the end portion may be provided without providing the joint portion 110.

　動圧発生用溝１２０は、シールリング１００における摺動面側の側面のうち合口部１１０付近を除く全周に亘って、等間隔に複数設けられている（図３参照）。これら複数の動圧発生用溝１２０は、軸２００に設けられた環状溝２１０における低圧側の側壁面２１１に対してシールリング１００が摺動した際に動圧を発生させるために設けられている。そして、動圧発生用溝１２０は、径方向の幅が一定で周方向に伸びる第１溝１２１と、第１溝１２１における周方向の中央の位置から内周面に至るまで伸び、密封対象流体を第１溝１２１内に導く第２溝１２２とから構成される。 A plurality of dynamic pressure generating grooves 120 are provided at equal intervals over the entire circumference of the seal ring 100 on the sliding surface side except for the vicinity of the joint portion 110 (see FIG. 3). The plurality of dynamic pressure generating grooves 120 are provided to generate dynamic pressure when the seal ring 100 slides with respect to the side wall surface 211 on the low pressure side in the annular groove 210 provided in the shaft 200. . The dynamic pressure generating groove 120 has a first groove 121 having a constant radial width and extending in the circumferential direction, and extends from the center position in the circumferential direction of the first groove 121 to the inner peripheral surface. And a second groove 122 that guides the light into the first groove 121.

　第１溝１２１は、環状溝２１０における低圧側の側壁面２１１に対して摺動する摺動領域Ｘ内に収まる位置に設けられている（図７参照）。また、第１溝１２１の溝深さについて、径方向に対しては深さが一定となるように構成されている（図５及び図７参照）。そして、第１溝１２１の溝深さについて、周方向に対しては、各種の構成を採用し得る。この点について、図８～図１２を参照して説明する。図８～図１１では、第１溝１２１の溝底が、周方向の中央に比べて両端側の方が浅くなるように構成された各種の例を示している。図８では、第１溝１２１の溝底が、周方向の中央から平面状に両側に向かって徐々に浅くなる場合の例を示している。図９では、第１溝１２１の溝底が、周方向の中央から曲面状に両側に向かって徐々に浅くなる場合の例を示している。図１０では、第１溝１２１の溝底が、周方向の中央から階段状に両側に向かって浅くなる場合の例を示している。図１１では、第１溝１２１の溝底が、周方向の中央から階段状に両側に向かって浅くなり、かつ段差部分が傾斜面で構成される場合の例を示している。このように、第１溝１２１の溝底が、周方向の中央に比べて両端側の方が浅くなるように構成することで、楔効果により動圧をより効果的に発生させることができる。ただし、図１２に示すように、第１溝１２１の溝底の深さが周方向に一定となるように構成した場合でも、ある程度動圧を発生させることは可能である。なお、本実施例における第１溝１２１は、最も深い部分でも５０μｍ以下となるように設定されている。 The first groove 121 is provided at a position that fits in the sliding region X that slides with respect to the low-pressure side wall surface 211 in the annular groove 210 (see FIG. 7). Further, the groove depth of the first groove 121 is configured to be constant in the radial direction (see FIGS. 5 and 7). And about the groove depth of the 1st groove | channel 121, various structures can be employ | adopted with respect to the circumferential direction. This point will be described with reference to FIGS. 8 to 11 show various examples in which the groove bottom of the first groove 121 is configured to be shallower at both ends compared to the center in the circumferential direction. FIG. 8 shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward both sides in a planar shape from the center in the circumferential direction. FIG. 9 shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a curved shape from the center in the circumferential direction. FIG. 10 shows an example in which the groove bottom of the first groove 121 becomes shallower toward both sides stepwise from the center in the circumferential direction. FIG. 11 shows an example in which the groove bottom of the first groove 121 becomes shallower toward the both sides in a stepwise manner from the center in the circumferential direction, and the stepped portion is formed of an inclined surface. In this way, the groove bottom of the first groove 121 is configured such that both ends are shallower than the center in the circumferential direction, so that dynamic pressure can be generated more effectively by the wedge effect. However, as shown in FIG. 12, even when the depth of the groove bottom of the first groove 121 is constant in the circumferential direction, it is possible to generate dynamic pressure to some extent. In addition, the 1st groove | channel 121 in a present Example is set so that it may become 50 micrometers or less even in the deepest part.

　＜シールリングの使用時のメカニズム＞
　特に、図７を参照して、本実施例に係るシールリング１００の使用時のメカニズムについて説明する。図７は、エンジンがかかり、シールリング１００を介して、差圧が生じている状態（図中右側の圧力が左側の圧力に比べて高くなった状態）を示している。エンジンがかかり、差圧が生じた状態においては、シールリング１００は、環状溝２１０の低圧側（Ｌ）の側壁面２１１及びハウジング３００の軸孔の内周面に対して密着した状態となる。 <Mechanism when using seal ring>
In particular, with reference to FIG. 7, the mechanism at the time of use of the seal ring 100 which concerns on a present Example is demonstrated. FIG. 7 shows a state in which the engine is started and a differential pressure is generated via the seal ring 100 (a state in which the pressure on the right side in the drawing is higher than the pressure on the left side). In a state where the engine is started and differential pressure is generated, the seal ring 100 is in close contact with the low-pressure side (L) side wall surface 211 of the annular groove 210 and the inner peripheral surface of the shaft hole of the housing 300.

　これにより、相対的に回転する軸２００とハウジング３００との間の環状隙間を封止して、流体圧力が変化するように構成されたシール対象領域（高圧側（Ｈ）の領域）の流体圧力を保持することが可能となる。そして、軸２００とハウジング３００が相対的に回転した場合には、環状溝２１０の低圧側（Ｌ）の側壁面２１１とシールリング１００との間で摺動する。そして、シールリング１００の摺動面側の側面に設けられた動圧発生用溝１２０から密封対象流体が摺動部分に流出する際に動圧が発生する。なお、シールリング１００が環状溝２１０に対して、図３中時計回り方向に回転する場合には、第１溝１２１における反時計回り方向側の端部から摺動部分に密封対象流体が流出する。また、シールリング１００が環状溝２１０に対して、図３中反時計回り方向に回転する場合には、第１溝１２１における時計回り方向側の端部から摺動部分に密封対象流体が流出する。 Thereby, the annular gap between the relatively rotating shaft 200 and the housing 300 is sealed, and the fluid pressure in the region to be sealed (the region on the high pressure side (H)) configured to change the fluid pressure. Can be held. When the shaft 200 and the housing 300 are relatively rotated, the shaft 200 slides between the side wall surface 211 on the low pressure side (L) of the annular groove 210 and the seal ring 100. Then, dynamic pressure is generated when the fluid to be sealed flows out from the dynamic pressure generating groove 120 provided on the sliding surface side surface of the seal ring 100 to the sliding portion. When the seal ring 100 rotates in the clockwise direction in FIG. 3 with respect to the annular groove 210, the fluid to be sealed flows out from the end portion of the first groove 121 on the counterclockwise direction side to the sliding portion. . When the seal ring 100 rotates counterclockwise in FIG. 3 with respect to the annular groove 210, the fluid to be sealed flows out from the end portion on the clockwise direction side of the first groove 121 to the sliding portion. .

　＜本実施例に係るシールリングの優れた点＞
　本実施例に係るシールリング１００によれば、動圧発生用溝１２０内に密封対象流体が導かれる。そのため、動圧発生用溝１２０が設けられている範囲においては、高圧側（Ｈ）からシールリング１００に対して作用する流体圧力と低圧側（Ｌ）からシールリング１００に対して作用する流体圧力が相殺される。これにより、シールリング１００に対する流体圧力（高圧側（Ｈ）から低圧側（Ｌ）への流体圧力）の受圧面積を減らすことができる。 <Excellent points of seal ring according to this embodiment>
According to the seal ring 100 according to the present embodiment, the fluid to be sealed is guided into the dynamic pressure generating groove 120. Therefore, in the range where the dynamic pressure generating groove 120 is provided, the fluid pressure acting on the seal ring 100 from the high pressure side (H) and the fluid pressure acting on the seal ring 100 from the low pressure side (L). Is offset. Thereby, the pressure receiving area of the fluid pressure (the fluid pressure from the high pressure side (H) to the low pressure side (L)) with respect to the seal ring 100 can be reduced.

　また、シールリング１００が環状溝２１０における低圧側の側壁面２１１に対して摺動する際に、第１溝１２１から摺動部分に密封対象流体が流出する際に動圧が発生する。これにより、シールリング１００に対して側壁面２１１から離れる方向の力が発生する。 Further, when the seal ring 100 slides with respect to the low-pressure side wall surface 211 in the annular groove 210, dynamic pressure is generated when the fluid to be sealed flows from the first groove 121 to the sliding portion. Thereby, a force in a direction away from the side wall surface 211 is generated with respect to the seal ring 100.

　以上のように、受圧面積が減ることと、動圧によりシールリング１００に対して側壁面２１１から離れる方向に力が発生することとが相俟って、回転トルクを効果的に低減させることが可能となる。このように、回転トルク（摺動トルク）の低減を実現できることにより、摺動による発熱を抑制することができ、高速高圧の環境条件下でも本実施例に係るシールリング１００を好適に用いることが可能となる。また、これに伴い、軸２００の材料としてアルミニウムなどの軟質材を用いることもできる。 As described above, combined with the reduction of the pressure receiving area and the generation of force in the direction away from the side wall surface 211 with respect to the seal ring 100 due to the dynamic pressure, it is possible to effectively reduce the rotational torque. It becomes possible. As described above, the reduction in rotational torque (sliding torque) can be realized, so that heat generated by sliding can be suppressed, and the seal ring 100 according to the present embodiment can be suitably used even under high-speed and high-pressure environmental conditions. It becomes possible. Accordingly, a soft material such as aluminum can be used as the material of the shaft 200.

　また、動圧発生用溝１２０は、第１溝１２１と、第１溝１２１の周方向の中央から内周面に至るまで伸びる第２溝１２２とを備える構成である。従って、環状溝２１０に対するシールリング１００の回転方向に関係なく、上記の動圧が発生する。 The dynamic pressure generating groove 120 includes a first groove 121 and a second groove 122 extending from the circumferential center of the first groove 121 to the inner peripheral surface. Accordingly, the dynamic pressure is generated regardless of the rotation direction of the seal ring 100 with respect to the annular groove 210.

　更に、第１溝１２１は、側壁面２１１に対して摺動する摺動領域Ｘ内に収まる位置に設けられているので、密封対象流体の漏れを抑制することができる。 Furthermore, since the first groove 121 is provided at a position within the sliding region X that slides with respect to the side wall surface 211, leakage of the fluid to be sealed can be suppressed.

　そして、図８～図１１に示すように、第１溝１２１の溝底が、周方向の中央に比べて両端側の方が浅くなるように構成すれば、楔効果により、上記の動圧を効果的に発生させることができる。特に、図８及び図９に示すように、第１溝１２１の溝底が、周方向の中央から両側に向かって徐々に浅くなる構成を採用した場合には、シールリング１００における摺動側の側面が経時的に摩耗が進んでしまっても、楔効果を安定的に発揮させることが可能である。 Then, as shown in FIGS. 8 to 11, if the groove bottom of the first groove 121 is configured to be shallower at both ends compared to the center in the circumferential direction, the above-described dynamic pressure is reduced by the wedge effect. It can be generated effectively. In particular, as shown in FIGS. 8 and 9, when a configuration in which the groove bottom of the first groove 121 gradually becomes shallower from the center in the circumferential direction toward both sides is adopted, Even if the side surface wears over time, the wedge effect can be stably exhibited.

　（実施例２）
　図１３～図１９は、本発明の実施例２が示されている。本実施例においては、動圧発生用溝について、第１溝のうち第２溝と繋がる部分の深さを、第２溝の深さと同じにし、かつ、第１溝における第２溝と繋がる部分以外の部分の深さよりも深く構成した場合の構成を示す。その他の構成および作用については実施例１と同一なので、同一の構成部分については同一の符号を付して、その説明は省略する。 (Example 2)
13 to 19 show a second embodiment of the present invention. In this embodiment, for the dynamic pressure generating groove, the depth of the portion connected to the second groove in the first groove is the same as the depth of the second groove, and the portion connected to the second groove in the first groove. The structure at the time of constructing deeper than the depth of the part other than is shown. Since other configurations and operations are the same as those in the first embodiment, the same components are denoted by the same reference numerals and description thereof is omitted.

　図１３は本発明の実施例２に係るシールリングの側面図の一部拡大図であり、上記実施例１における図４に相当する図である。図１４～図１９は本発明の実施例２に係るシールリングの模式的断面図である。なお、図１４～図１９は図１３中のＣＣ断面図である。 FIG. 13 is a partially enlarged view of a side view of the seal ring according to the second embodiment of the present invention, which corresponds to FIG. 4 in the first embodiment. 14 to 19 are schematic sectional views of a seal ring according to Embodiment 2 of the present invention. 14 to 19 are CC sectional views in FIG.

　本実施例においては、動圧発生用溝の構成についてのみ、実施例１の場合と異なっており、その他の構成については、実施例１と同一であるので、その説明は省略する。本実施例に係るシールリング１００においても、動圧発生用溝１２０は、シールリング１００における摺動面側の側面のうち合口部１１０付近を除く全周に亘って、等間隔に複数設けられている。また、実施例１の場合と同様に、動圧発生用溝１２０は、径方向の幅が一定で周方向に伸びる第１溝１２１と、第１溝１２１における周方向の中央の位置から内周面に至るまで伸び、密封対象流体を第１溝１２１内に導く第２溝１２２とから構成される。 In the present embodiment, only the configuration of the dynamic pressure generating groove is different from that in the first embodiment, and the other configurations are the same as those in the first embodiment, and thus the description thereof is omitted. Also in the seal ring 100 according to the present embodiment, a plurality of dynamic pressure generating grooves 120 are provided at equal intervals over the entire circumference except for the vicinity of the joint portion 110 in the side surface of the seal ring 100 on the sliding surface side. Yes. Similarly to the case of the first embodiment, the dynamic pressure generating groove 120 includes a first groove 121 having a constant radial width and extending in the circumferential direction, and an inner circumference from a center position in the circumferential direction of the first groove 121. The second groove 122 extends to the surface and guides the fluid to be sealed into the first groove 121.

　また、第１溝１２１が、環状溝２１０における低圧側の側壁面２１１に対して摺動する摺動領域Ｘ内に収まる位置に設けられている点についても、実施例１の場合と同様である（図７参照）。また、第１溝１２１の溝深さについて、径方向に対しては深さが一定となるように構成されている点も、実施例１の場合と同様である。 Further, the first groove 121 is also provided at a position that fits within the sliding region X that slides with respect to the low-pressure side wall surface 211 in the annular groove 210 as in the case of the first embodiment. (See FIG. 7). Further, the groove depth of the first groove 121 is the same as that of the first embodiment in that the depth is configured to be constant in the radial direction.

　そして、本実施例に係る動圧発生用溝１２０においては、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが、第２溝１２２の深さと同じで、かつ、第１溝１２１における第２溝１２２と繋がる部分以外の部分１２１Ｙの深さよりも深く構成されている。第１溝１２１の溝深さについて、周方向に対しては、各種の構成を採用し得る。この点について、図１４～図１９を参照して説明する。 In the dynamic pressure generating groove 120 according to the present embodiment, the depth of the portion 121X of the first groove 121 connected to the second groove 122 is the same as the depth of the second groove 122, and the first groove 121 is configured to be deeper than the depth of the portion 121 </ b> Y other than the portion connected to the second groove 122. About the groove depth of the 1st groove | channel 121, various structures can be employ | adopted with respect to the circumferential direction. This point will be described with reference to FIGS.

　図１４～図１９では、第１溝１２１の溝底が、周方向の中央に比べて両端側の方が浅くなるように構成された各種の例を示している。図１４は実施例１における図８に示す例の変形例であり、第１溝１２１の溝底が、周方向の中央から平面状に両側に向かって徐々に浅くなる場合の例を示している。そして、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが他の部分１２１Ｙに比べてより一段と深くなっている。図１５は実施例１における図９に示す例の変形例であり、第１溝１２１の溝底が、周方向の中央から曲面状に両側に向かって徐々に浅くなる場合の例を示している。そして、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが他の部分１２１Ｙに比べてより一段と深くなっている。図１６は実施例１における図１０に示す例の変形例であり、第１溝１２１の溝底が、周方向の中央から階段状に両側に向かって浅くなる場合の例を示している。そして、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが他の部分１２１Ｙに比べてより一段と深くなっている。 FIGS. 14 to 19 show various examples in which the groove bottom of the first groove 121 is configured to be shallower at both ends compared to the center in the circumferential direction. FIG. 14 is a modification of the example shown in FIG. 8 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a planar shape from the center in the circumferential direction. . And the depth of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 is deeper than the other part 121Y. FIG. 15 is a modification of the example shown in FIG. 9 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a curved shape from the center in the circumferential direction. . And the depth of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 is deeper than the other part 121Y. FIG. 16 is a modification of the example shown in FIG. 10 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 becomes shallower toward both sides stepwise from the center in the circumferential direction. And the depth of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 is deeper than the other part 121Y.

　図１７は実施例１における図８に示す例の変形例であり、第１溝１２１の溝底が、周方向の中央から平面状に両側に向かって徐々に浅くなる場合の例を示している。そして、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが他の部分１２１Ｙに比べてより一段と深くなっている。また、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの溝底が湾曲面となるように構成されている。図１８は実施例１における図９に示す例の変形例であり、第１溝１２１の溝底が、周方向の中央から曲面状に両側に向かって徐々に浅くなる場合の例を示している。そして、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが他の部分１２１Ｙに比べてより一段と深くなっている。また、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの溝底が湾曲面となるように構成されている。図１９は実施例１における図１０に示す例の変形例であり、第１溝１２１の溝底が、周方向の中央から階段状に両側に向かって浅くなる場合の例を示している。そして、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが他の部分１２１Ｙに比べてより一段と深くなっている。また、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの溝底が湾曲面となるように構成されている。 FIG. 17 is a modification of the example shown in FIG. 8 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a planar shape from the center in the circumferential direction. . And the depth of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 is deeper than the other part 121Y. Moreover, it is comprised so that the groove bottom of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 may become a curved surface. FIG. 18 is a modification of the example shown in FIG. 9 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 gradually becomes shallower toward the both sides in a curved shape from the center in the circumferential direction. . And the depth of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 is deeper than the other part 121Y. Moreover, it is comprised so that the groove bottom of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 may become a curved surface. FIG. 19 is a modification of the example shown in FIG. 10 in the first embodiment, and shows an example in which the groove bottom of the first groove 121 becomes shallower toward both sides stepwise from the center in the circumferential direction. And the depth of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 is deeper than the other part 121Y. Moreover, it is comprised so that the groove bottom of the part 121X connected with the 2nd groove | channel 122 among the 1st groove | channels 121 may become a curved surface.

　なお、本実施例に係る第１溝１２１のうち第２溝１２２と繋がる部分以外の部分１２１Ｙの深さは、最も深い部分でも５０μｍ以下となるように設定されている。 Note that the depth of the portion 121Y other than the portion connected to the second groove 122 in the first groove 121 according to the present embodiment is set to be 50 μm or less even at the deepest portion.

　以上のように構成された本実施例に係るシールリング１００によれば、動圧発生用溝１２０における第２溝１２２の深さと、第１溝１２１のうち第２溝１２２と繋がる部分１２１Ｘの深さが深いため、密封対象流体の導入量を高めることができる。これにより、動圧発生用溝１２０による動圧発生効果を高めることができる。 According to the seal ring 100 according to the present embodiment configured as described above, the depth of the second groove 122 in the dynamic pressure generating groove 120 and the depth of the portion 121X of the first groove 121 connected to the second groove 122. Therefore, the amount of fluid to be sealed can be increased. Thereby, the dynamic pressure generation effect by the dynamic pressure generation groove 120 can be enhanced.

　１００　シールリング
　１１０　合口部
　１２０　動圧発生用溝
　１２１　第１溝
　１２２　第２溝
　２００　軸
　２１０　環状溝
　２１１　側壁面
　３００　ハウジング
　Ｘ　摺動領域 DESCRIPTION OF SYMBOLS 100 Seal ring 110 Joint part 120 Dynamic pressure generating groove 121 1st groove 122 2nd groove 200 Shaft 210 Annular groove 211 Side wall surface 300 Housing X Sliding area

Claims (2)

　軸の外周に設けられた環状溝に装着され、相対的に回転する前記軸とハウジングとの間の環状隙間を封止して、流体圧力が変化するように構成されたシール対象領域の流体圧力を保持するシールリングであって、
　前記環状溝における低圧側の側壁面に対して摺動するシールリングにおいて、
　前記側壁面に対して摺動する摺動面側には、径方向の幅が一定で周方向に伸びる第１溝と、第１溝における周方向の中央の位置から内周面に至るまで伸び、密封対象流体を第１溝内に導く第２溝とを有する動圧発生用溝が設けられており、
　第１溝は、前記側壁面に対して摺動する摺動領域内に収まる位置に設けられていることを特徴とするシールリング。 Fluid pressure in a region to be sealed is mounted in an annular groove provided on the outer periphery of the shaft and configured to seal the annular clearance between the relatively rotating shaft and the housing so that the fluid pressure changes. A seal ring for holding
In the seal ring that slides against the side wall surface on the low pressure side in the annular groove,
On the sliding surface side that slides with respect to the side wall surface, a first groove having a constant radial width and extending in the circumferential direction, and extending from the center position in the circumferential direction of the first groove to the inner peripheral surface. , A dynamic pressure generating groove having a second groove for guiding the fluid to be sealed into the first groove is provided,
The seal ring according to claim 1, wherein the first groove is provided in a position within a sliding region that slides with respect to the side wall surface. 　第１溝の溝底は、周方向の中央に比べて両端側の方が浅くなるように構成されていることを特徴とする請求項１に記載のシールリング。 2. The seal ring according to claim 1, wherein the groove bottom of the first groove is configured so that both ends are shallower than the center in the circumferential direction.
PCT/JP2015/051869 2014-01-24 2015-01-23 Seal ring Ceased WO2015111707A1 (en)

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EP15740299.1A EP3098486B1 (en) 2014-01-24 2015-01-23 Sealing ring
KR1020167019126A KR20160098451A (en) 2014-01-24 2015-01-23 Seal ring
US15/113,506 US10865883B2 (en) 2014-01-24 2015-01-23 Sealing ring
CN201580005061.XA CN105917151A (en) 2014-01-24 2015-01-23 sealing ring
JP2015559134A JP6298834B2 (en) 2014-01-24 2015-01-23 Seal ring

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JP2017172606A (en) * 2016-03-18 2017-09-28 株式会社リケン Seal ring
US20180058584A1 (en) * 2015-03-16 2018-03-01 Nok Corporation Seal ring
EP3273115A4 (en) * 2015-03-16 2018-10-24 Nok Corporation Seal ring
EP3299685A4 (en) * 2015-05-19 2018-12-05 Eagle Industry Co., Ltd. Sliding component
WO2019059341A1 (en) * 2017-09-21 2019-03-28 Nok株式会社 Seal ring
EP3385577A4 (en) * 2015-12-03 2019-07-03 NOK Corporation Shaft and seal structure
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